EP0857255B1 - Feeding pump - Google Patents
Feeding pump Download PDFInfo
- Publication number
- EP0857255B1 EP0857255B1 EP97922837A EP97922837A EP0857255B1 EP 0857255 B1 EP0857255 B1 EP 0857255B1 EP 97922837 A EP97922837 A EP 97922837A EP 97922837 A EP97922837 A EP 97922837A EP 0857255 B1 EP0857255 B1 EP 0857255B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- channel
- damping groove
- communication
- side channel
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D5/00—Pumps with circumferential or transverse flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D5/00—Pumps with circumferential or transverse flow
- F04D5/002—Regenerative pumps
Definitions
- the invention is based on a flow pump, especially for delivering fuel from a Fuel tank of a motor vehicle, which in the preamble of Claim 1 defined genus.
- peripheral pump In a known two-flow flow pump of this type (DE 40 20 521 A1), there called peripheral pump, is from one side wall of the walls delimiting the pump chamber and the peripheral wall at a the pump outlet having intermediate housing and the other side wall one connected to an outlet nozzle Housing cover formed with pump inlet.
- the Pump or impeller arranged in the pump chamber is seated a molded on the housing cover and is rotatably with the output shaft of an electric motor connected, which is formed in an intermediate housing Depository is added. The sucks during operation Flow pump fuel on the intake manifold on and presses this into the interior of a via the pump outlet Enclosing electric motor and intermediate housing Pump housing. From there it is under pressure standing fuel over a at a pressure port of the Pump housing to be connected to the pressure line of the Internal combustion engine supplied.
- This known flow pump shows the geometrical Design of the outlet area of the side channel in the good noise behavior on both side walls.
- the flow pump according to the invention with the characteristic Features of claim 1 has the advantage that the of Flow pump still caused flow-induced Noises are further reduced.
- the Damping groove according to the invention which by their arrangement according to the invention in the region of the largest occurring amplitudes of the wall pressure vibrations with Impeller blade frequency, the wall alternating pressures significantly reduced what with a clear Noise reduction goes hand in hand.
- the flow pump seen in side view in FIG. 1, also called side channel pump, is used to pump Fuel from a fuel tank, not shown of a motor vehicle to a likewise not shown Internal combustion engine of the motor vehicle.
- the flow pump has a formed in a pump housing 10 Pump chamber 11 that of two radially extending, axially spaced side walls 12, 13 and one the side walls along their periphery with each other connecting peripheral wall 14 is limited (Fig. 1 and 2).
- the side wall 13 and the peripheral wall 14 are on one Intermediate housing 15 formed (Fig. 2 and 3), while the Side wall 12 on a suction or housing cover 16 (Fig. 4 and 5) which is formed with the intermediate housing 15 and / or the pump housing 10 is firmly connected.
- the Pump housing 10 overlaps the intermediate housing 15 and takes an electric motor not visible here inside on.
- the intermediate housing 15 there is also a side wall 13 axially penetrating pump outlet 17 is provided, the one Connection between the pump chamber 11 and the interior of the Manufactures pump housing 10, and the pump housing 10 is connected to a pressure port 18 on which the of the Flow pump delivered fuel exits.
- the Housing cover 16 has an intake port 19 for intake of the fuel from the fuel tank, which with a the pump inlet 33 penetrating the side wall 12 (FIG. 5) communicates.
- each side wall 12 13 has a side channel 20 or 21 educated.
- everyone Side channel 20, 21 runs concentrically to pump axis 22 and extends leaving one remaining Break bar 35 or 23 almost over the entire Circumference of the side wall 12 or 13.
- the interrupter web 35 is from the side channel start 201 and the side channel end 202 (Fig. 5), and according to the interrupter 23 from Side channel start 211 and side channel end 212 (FIG. 3) limited.
- the side channel start 201 of the side channel 20 in the side wall 12 on the housing cover 16 stands with the Pump inlet 33 (and this in turn with the intake manifold 19) and the side channel end 212 of the in the side wall 13 Intermediate housing 15 formed side channel 21 is available the pump outlet 17 in connection and this in turn the inside of the pump housing 10 with the pressure port 18.
- Impeller 24 arranged in the pump chamber 11 is a pump or coaxial to the pump axis 22 Impeller 24 arranged.
- the impeller 24 sits on the one hand on a bearing journal 25, which is coaxial on the side wall 12 protrudes into the pump chamber 11 and on the other hand rotatably on an output shaft 26 of the electric motor, the in a bearing bushing 27 coaxial to the pump axis 22 is stored.
- the bearing bush 27 is in a Sidewall 13 penetrating coaxial bore 28 in Pressed intermediate housing 15.
- the impeller 24 (Fig. 7) has a plurality of circumferentially from each other spaced impeller blades 29 at their from the Pump axis 22 opposite end by a circular Outer ring 30 are interconnected.
- the Impeller blades 29 each limit one between them Vane chamber 31, which is open in the axial direction.
- the Impeller blades 29 and the outer ring 30 are in one piece with the impeller 24, and the impeller blades 29 formed in that between on a common Distribution circuit arranged openings in the impeller 24 Web remain as impeller blades 29.
- the outer ring 30 is dimensioned so that between the circumferential outer surface 301 of the outer ring 30 and the peripheral wall 14 Radial gap 32 remains (Fig. 1). Sucks in operation Flow pump fuel through the intake 19 and presses the fuel through the pump outlet 17 into the Inside of the pump housing 10 and from there on Pressure port 18 to the internal combustion engine.
- curved damping groove 36 introduced (Fig. 5), the extends approximately across the side channel width. That in Fig. 5 side channel end of the side channel 20 identified by 202 has an approximately S-shaped curved contour, the middle part of the contour on the center line 37 of the Side channel 20 or parallel to it.
- the damping groove 36 is now such at the contour of the side channel end 202 along that the measured in the circumferential direction Distance dimension s between the center line 38 of the damping groove 36 and the contour of the side channel end 202 at each point the center line 38 is constant.
- the distance measure s is one to three times as large as that in Circumferential direction of the impeller 24 seen thickness ⁇ the Impeller blades 29.
- the shape of the damping groove 36 is there executed so that the outer and inner circular arc Boundary line of the damping groove 36 and the center line 38 the damping groove 36 the same center of curvature exhibit.
- the damping groove 36 has a semicircular cross section with the maximum groove depth t in the range of 0.1 - 1.5 mm, preferably between 0.2 mm and 0.5 mm.
- the maximum groove width b is one to three times that in Thickness ⁇ of the impeller blades 29 seen in the circumferential direction the impeller 24.
- damping groove 39 in the Side wall 13 of the intermediate housing 15 are introduced, here again in the interrupter 23 near the Side channel end 212 of the side channel 21.
- the pump outlet 17 opens here.
- the damping groove 39 is identical to the damping groove 36, so that the design information given there also apply here.
- the flow pump can the damping groove 36 in the side wall 12 of the housing cover 16 omitted, so that only - as described above - the Damping groove 36 in the side wall 13 of the intermediate housing 15 is available.
- the invention is not based on those described Embodiments limited. So the flow pump can also be executed with one flow, so that only in one Sidewall there is a side channel, the Side channel start with the pump inlet and its Side channel end is connected to the pump outlet.
- the side channel can be in the intermediate housing or in Housing cover are formed.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
Die Erfindung geht aus von einer Strömungspumpe, insbesondere zum Fördern von Kraftstoff aus einem Kraftstofftank eines Kraftfahrzeugs, der im Oberbegriff des Anspruchs 1 definierten Gattung.The invention is based on a flow pump, especially for delivering fuel from a Fuel tank of a motor vehicle, which in the preamble of Claim 1 defined genus.
Bei einer bekannten zweiflutigen Strömungspumpe dieser Art (DE 40 20 521 A1), dort Peripheralpumpe genannt, ist von den den Pumpenraum begrenzenden Wänden die eine Seitenwand und die Peripherwand an einem den Pumpenausgang aufweisenden Zwischengehäuse und die andere Seitenwand an einem den mit einem Ausgangsstutzen verbundenen Pumpeneingang aufweisenden Gehäusedeckel ausgebildet. Das im Pumpenraum angeordnete Pumpen- oder Laufrad sitzt auf einem an dem Gehäusedeckel angeformten Lagerzapfen und ist drehfest mit der Abtriebswelle eines Elektromotors verbunden, die in einer im Zwischengehäuse ausgebildeten Lagerstelle aufgenommen ist. Während des Betriebs saugt die Strömungspumpe Kraftstoff über den Ansaugstutzen an und drückt diesen über den Pumpenausgang in den Innenraum eines Elektromotors und Zwischengehäuse umschließenden Pumpengehäuses. Von diesem aus wird der unter Druck stehende Kraftstoff über eine an einem Druckstutzen des Pumpengehäuses anzuschließende Druckleitung der Brennkraftmaschine zugeführt.In a known two-flow flow pump of this type (DE 40 20 521 A1), there called peripheral pump, is from one side wall of the walls delimiting the pump chamber and the peripheral wall at a the pump outlet having intermediate housing and the other side wall one connected to an outlet nozzle Housing cover formed with pump inlet. The Pump or impeller arranged in the pump chamber is seated a molded on the housing cover and is rotatably with the output shaft of an electric motor connected, which is formed in an intermediate housing Depository is added. The sucks during operation Flow pump fuel on the intake manifold on and presses this into the interior of a via the pump outlet Enclosing electric motor and intermediate housing Pump housing. From there it is under pressure standing fuel over a at a pressure port of the Pump housing to be connected to the pressure line of the Internal combustion engine supplied.
Diese bekannte Strömungspumpe zeigt durch die geometrische Gestaltung des Auslaufbereichs des Seitenkanals in den beiden Seitenwänden ein gutes Geräuschverhalten.This known flow pump shows the geometrical Design of the outlet area of the side channel in the good noise behavior on both side walls.
Die erfindungsgemäße Strömungspumpe mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, daß die von der Strömungspumpe noch verursachten strömungsinduzierten Geräusche weitergehend reduziert sind. Durch die erfindungsgemäße Dämpfungsnut, die durch ihre erfindungsgemäße Anordnung im Bereich der größten auftretenden Amplituden der Wanddruckschwingungen mit Laufradschaufelfrequenz liegt, werden die Wandwechseldrücke maßgeblich reduziert, was mit einer deutlichen Geräuschverminderung einhergeht. Zusätzlich ergibt sich der Vorteil, daß größere Axialspalte zwischen dem Laufrad und den den Laufradstirnseiten gegenüberliegende Seitenwänden zugelassen werden können, was zu einer größeren zulässigen Fertigungstoleranz und damit zu einer Senkung der Herstellkosten führt.The flow pump according to the invention with the characteristic Features of claim 1 has the advantage that the of Flow pump still caused flow-induced Noises are further reduced. Through the Damping groove according to the invention, which by their arrangement according to the invention in the region of the largest occurring amplitudes of the wall pressure vibrations with Impeller blade frequency, the wall alternating pressures significantly reduced what with a clear Noise reduction goes hand in hand. In addition, the Advantage that larger axial gaps between the impeller and the side walls opposite the impeller end faces can be approved, resulting in a larger allowable Manufacturing tolerance and thus a reduction in Manufacturing costs leads.
Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Strömungspumpe möglich. By the measures listed in the other claims are advantageous developments and improvements in Claim 1 specified flow pump possible.
Die Erfindung ist anhand eines in der Zeichnung dargestellten Ausführungsbeispiel in der nachfolgenden Beschreibung näher erläutert. Es zeigen:
- Fig. 1
- eine Seitenansicht einer Strömungspumpe zum Fördern von Kraftstoff, teilweise geschnitten,
- Fig. 2
- einen Schnitt längs der Linie II-II in Fig. 3 eines Zwischengehäuses in der Strömungspumpe in Fig. 1
- Fig. 3
- eine Ansicht des Zwischengehäuses in Richtung Pfeil III in Fig. 2,
- Fig. 4
- einen Schnitt längs der Linie IV-IV in Fig. 5 eines Gehäusedeckels der Strömungspumpe in Fig. 1,
- Fig. 5
- eine Ansicht des Gehäusedeckels in Richtung Pfeil V in Fig. 4,
- Fig. 6
- einen Schnitt längs der Linie VI-VI in Fig. 5,
- Fig. 7
- eine Seitenansicht eines Laufrads der Strömungspumpe in Fig. 1.
- Fig. 1
- a side view of a flow pump for conveying fuel, partially cut,
- Fig. 2
- 3 shows a section along the line II-II in FIG. 3 of an intermediate housing in the flow pump in FIG. 1
- Fig. 3
- 2 shows a view of the intermediate housing in the direction of arrow III in FIG. 2,
- Fig. 4
- 5 shows a section along the line IV-IV in FIG. 5 of a housing cover of the flow pump in FIG. 1,
- Fig. 5
- 3 shows a view of the housing cover in the direction of arrow V in FIG. 4,
- Fig. 6
- a section along the line VI-VI in Fig. 5,
- Fig. 7
- 2 shows a side view of an impeller of the flow pump in FIG. 1.
Die in Fig. 1 in Seitenansicht zu sehende Strömungspumpe,
auch Seitenkanalpumpe genannt, dient zum Fördern von
Kraftstoff aus einem nicht dargestellten Kraftstofftank
eines Kraftfahrzeugs zu einer ebenfalls nicht dargestellten
Brennkraftmaschine des Kraftfahrzeugs. Die Strömungspumpe
weist einen in einem Pumpengehäuse 10 ausgebildeten
Pumpenraum 11 auf, der von zwei radial sich erstreckenden,
axial voneinander beabstandeten Seitenwänden 12,13 und
einer die Seitenwände längs deren Peripherie miteinander
verbindenden Peripherwand 14 begrenzt ist (Fig. 1 und 2).
Die Seitenwand 13 und die Peripherwand 14 sind an einem
Zwischengehäuse 15 ausgebildet (Fig. 2 und 3), während die
Seitenwand 12 an einem Ansaug- oder Gehäusedeckel 16 (Fig.
4 und 5) ausgebildet ist, der mit dem Zwischengehäuse 15
und/oder dem Pumpengehäuse 10 fest verbunden ist. Das
Pumpengehäuse 10 übergreift das Zwischengehäuse 15 und
nimmt im Innern einen hier nicht zu sehenden Elektromotor
auf. Im Zwischengehäuse 15 ist noch ein die Seitenwand 13
axial durchdringender Pumpenausgang 17 vorgesehen, der eine
Verbindung zwischen dem Pumpenraum 11 und dem Innern des
Pumpengehäuses 10 herstellt, und das Pumpengehäuse 10 ist
mit einem Druckstutzen 18 verbunden, an dem der von der
Strömungspumpe geförderte Kraftstoff austritt. Der
Gehäusedeckel 16 weist einen Ansaugstutzen 19 zum Ansaugen
des Kraftstoffs aus dem Kraftstofftank auf, der mit einem
die Seitenwand 12 durchdringenden Pumpeneingang 33 (Fig. 5)
in Verbindung steht.The flow pump seen in side view in FIG. 1,
also called side channel pump, is used to pump
Fuel from a fuel tank, not shown
of a motor vehicle to a likewise not shown
Internal combustion engine of the motor vehicle. The flow pump
has a formed in a
Bei der hier zweiflutig ausgebildeten Strömungspumpe ist in
jeder Seitenwand 12,13 ein Seitenkanal 20 bzw. 21
ausgebildet. Wie in Fig. 4 und 2 zu sehen ist, weist jeder
nutartige Seitenkanal 20,21 einen etwa halbkreisförmigen
Querschnitt auf und ist zum Pumpenraum 11 hin offen. Jeder
Seitenkanal 20,21 verläuft konzentrisch zur Pumpenachse 22
und erstreckt sich unter Belassung eines verbleibenden
Unterbrecherstegs 35 bzw. 23 nahezu über den gesamten
Umfang der Seitenwand 12 bzw. 13. Der Unterbrechersteg 35
wird vom Seitenkanalanfang 201 und dem Seitenkanalende 202
(Fig. 5), und entsprechend der Unterbrechersteg 23 vom
Seitenkanalanfang 211 und dem Seitenkanalende 212 (Fig. 3)
begrenzt. Der Seitenkanalanfang 201 des Seitenkanals 20 in
der Seitenwand 12 am Gehäusedeckel 16 steht mit dem
Pumpeneingang 33 (und dieser wiederum mit dem Ansaugstutzen
19) und das Seitenkanalende 212 des in der Seitenwand 13 am
Zwischengehäuse 15 ausgebildeten Seitenkanals 21 steht mit
dem Pumpenausgang 17 in Verbindung und dieser wiederum über
das Innere des Pumpengehäuses 10 mit dem Druckstutzen 18.In the case of the flow pump designed here with two flow channels, in
each
Im Pumpenraum 11 ist koaxial zur Pumpenachse 22 ein Pumpenoder
Laufrad 24 angeordnet. Das Laufrad 24 sitzt einerseits
auf einem Lagerzapfen 25, der an der Seitenwand 12 koaxial
in den Pumpenraum 11 hinein vorsteht und andererseits
drehfest auf einer Abtriebswelle 26 des Elektromotors, die
in einer zur Pumpenachse 22 koaxialen Lagerbuchse 27
gelagert ist. Die Lagerbuchse 27 ist in einer die
Seitenwand 13 durchstoßenden koaxialen Bohrung 28 im
Zwischengehäuse 15 eingepreßt. Das Laufrad 24 (Fig. 7)
besitzt eine Vielzahl von in Umfangsrichtung voneinander
beabstandeten Laufradschaufeln 29, die an ihrem von der
Pumpenachse 22 abgekehrten Ende durch einen kreisförmigen
Außenring 30 miteinander verbunden sind. Die
Laufradschaufeln 29 begrenzen zwischen sich jeweils eine
Schaufelkammer 31, die in Achsrichtung offen ist. Die
Laufradschaufeln 29 und der Außenring 30 sind einstückig
mit dem Laufrad 24, und die Laufradschaufeln 29 sind
dadurch gebildet, daß zwischen auf einem gemeinsamen
Verteilerkreis angeordneten Durchbrüchen im Laufrad 24
Stege als Laufradschaufeln 29 verbleiben. Der Außenring 30
ist so bemessen, daß zwischen der umlaufenden Außenfläche
301 des Außenrings 30 und der Peripherwand 14 ein
Radialspalt 32 verbleibt (Fig. 1). Im Betrieb saugt die
Strömungspumpe Kraftstoff durch den Ansaugstutzen 19 an und
drückt den Kraftstoff über den Pumpenausgang 17 in das
Innere des Pumpengehäuses 10 und von dort aus über den
Druckstutzen 18 zur Brennkraftmaschine. In the
Um die lokal sehr hohen Druckamplituden der
Schaufelfrequenzschwingung deutlich zu reduzieren und damit
die Strömungspumpe wesentlich geräuschärmer zu machen, ist
in den den Seitenkanal 20 in der Seitenwand 12 am Ansaugoder
Gehäusedeckel 16 eine zum Pumpenraum 11 hin offene,
gekrümmte Dämpfungsnut 36 eingebracht (Fig. 5), die sich
etwa über die Seitenkanalbreite erstreckt. Das in Fig. 5
mit 202 gekennzeichnete Seitenkanalende des Seitenkanals 20
hat eine etwa S-förmige gekrümmte Kontur, wobei der
mittlere Teil der Kontur auf der Mittellinie 37 des
Seitenkanals 20 oder parallel dazu liegt. Die Dämpfungsnut
36 ist nunmehr derart an der Kontur des Seitenkanalendes
202 entlanggeführt, daß das in Umfangsrichtung gemessene
Abstandsmaß s zwischen der Mittellinie 38 der Dämpfungsnut
36 und der Kontur des Seitenkanalendes 202 an jedem Punkt
der Mittellinie 38 konstant ist. Das Abstandsmaß s wird
dabei ein- bis dreimal so groß bemessen wie die in
Umfangsrichtung des Laufrads 24 gesehene Dicke δ der
Laufradschaufeln 29. Die Form der Dämpfungsnut 36 ist dabei
so ausgeführt, daß die äußere und innere kreisbogenförmige
Begrenzungslinie der Dämpfungsnut 36 und die Mittellinie 38
der Dämpfungsnut 36 den gleichen Krümmungsmittelpunkt
aufweisen.To the locally very high pressure amplitudes of the
To reduce blade frequency vibration significantly and thus
to make the flow pump much quieter
in the
Wie aus der Schnittdarstellung in Fig. 6 hervorgeht, weist
die Dämpfungsnut 36 einen halbkreisförmigen Querschnitt
auf, wobei die maximale Nuttiefe t im Bereich von 0,1 -
1,5mm, vorzugsweise zwischen 0,2 mm und 0,5 mm, liegt. Die
maximale Nutbreite b beträgt das Ein- bis Dreifache der in
Umfangsrichtung gesehenen Dicke δ der Laufradschaufeln 29
des Laufrads 24.As can be seen from the sectional view in FIG. 6, points
the damping
Wie in Fig. 3 dargestellt ist, kann zusätzlich zu der
Dämpfungsnut 36 in der Seitenwand 12 des Gehäusedeckels 16
eine gleichartig ausgebildete Dämpfungsnut 39 in die
Seitenwand 13 des Zwischengehäuses 15 eingebracht werden,
auch hier wiederum im Unterbrechersteg 23 nahe dem
Seitenkanalende 212 des Seitenkanals 21. Wie bereits
erwähnt, mündet hier der Pumpenausgang 17. Die Dämpfungsnut
39 ist identisch der Dämpfungsnut 36 ausgebildet, so daß
die dort genannten Bemessungsangaben auch hier zutreffen.As shown in Fig. 3, in addition to that
Damping
In einer alternativen Ausführung der Strömungspumpe kann
die Dämpfungsnut 36 in der Seitenwand 12 des Gehäusedeckels
16 entfallen, so daß nur - wie vorstehend beschrieben - die
Dämpfugsnut 36 in der Seitenwand 13 des Zwischengehäuses 15
vorhanden ist.In an alternative embodiment, the flow pump can
the damping
Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt. So kann die Strömungspumpe auch einflutig ausgeführt werden, so daß nur in einer Seitenwand ein Seitenkanal vorhanden ist, dessen Seitenkanalanfang mit dem Pumpeneingang und dessen Seitenkanalende mit dem Pumpenausgang in Verbindung steht. Der Seitenkanal kann dabei im Zwischengehäuse oder im Gehäusedeckel ausgebildet werden.The invention is not based on those described Embodiments limited. So the flow pump can also be executed with one flow, so that only in one Sidewall there is a side channel, the Side channel start with the pump inlet and its Side channel end is connected to the pump outlet. The side channel can be in the intermediate housing or in Housing cover are formed.
Claims (11)
- Flow pump, in particular for delivering fuel from a fuel tank of a motor vehicle, having a pump chamber (11), which is formed in a pump housing (10) and is delimited by two side walls (20, 21), which extend in the radial direction and are spaced apart from one another, and one peripheral wall (14), which connects the side walls (20, 21) to one another along the periphery thereof, having at least one groove-like side channel (20, 21), which is arranged in one of the side walls (12, 13), is open towards the pump chamber (11) and runs concentrically with respect to the pump axis (22), with an interrupter web (35, 23) remaining between the side-channel end (202, 212) and the side-channel start (201, 211), based on the direction of flow in the side channel (20, 21), and having a rotor (24), which is arranged in the pump chamber (11), coaxially with respect to the pump axis (22), rotates and has a multiplicity of radial rotor blades (29), which are spaced apart from one another in the circumferential direction and delimit at least axially open blade chambers (31) between them, characterized in that a damping groove (36), which is open towards the pump chamber (11), is formed in the interrupter web (35), close to the side-channel end (202), this groove extending over approximately the width of the side channel.
- Pump according to Claim 1, characterized in that the damping groove (36) is guided along the contour of the side-channel end (202) in such a manner that the distance (s), measured in the circumferential direction, between the centre line (38) of the damping groove (36) and the contour of the side-channel end (202) is constant at any point along the centre line (38).
- Pump according to Claim 2, characterized in that the boundary lines, lying on either side of the centre line (38), of the damping groove (36) and the centre line (38) have the same centre of curvature.
- Pump according to Claim 2 or 3, characterized in that the distance (s) is one to three times the thickness (δ), as seen in the circumferential direction of the rotor (24), of the rotor blades (29) of the rotor (24).
- Pump according to one of Claims 1-4, characterized in that the damping groove (36) has a semicircular cross section.
- Pump according to one of Claims 1-5, characterized in that the maximum groove depth (t) of the damping groove (36) is in the range from 0.1 - 1.5 mm, preferably between 0.2 - 0.5 mm.
- Pump according to one of Claims 1-6, characterized in that the maximum groove width (b) of the damping groove (36) is one to three times the thickness (δ), as seen in the circumferential direction, of the rotor blades (29) of the rotor (24).
- Pump according to one of Claims 1-7, characterized in that there is a side channel (20, 21) in each side wall (12, 13), and the side-channel start (201) of one side channel (20) is in communication with a pump inlet (33), and the side-channel end (212) of the other side channel (21) is in communication with a pump outlet (17), and in that the damping groove (36) is arranged in the interrupter web (35) of that side channel (20) whose side-channel start (201) is in communication with the pump inlet (33).
- Pump according to one of Claims 1-7, characterized in that there is a side channel (20, 21) in each side wall (12, 13), and the side-channel start (201) of one side channel (20) is in communication with a pump inlet (33), and the side-channel end (212) of the other side channel (21) is in communication with a pump outlet (17), and in that the damping groove (39) is arranged in the interrupter web (23) of that side channel (21) whose side-channel end (212) is in communication with the pump outlet (17).
- Pump according to one of Claims 1-7, characterized in that there is a side channel (20, 21) in each side wall (12, 13), and the side-channel start (201) of one side channel (20) is in communication with a pump inlet (33), and the side-channel end (212) of the other side channel (21) is in communication with a pump outlet (17), and in that a similar damping groove (36, 39) is arranged in the interrupter web (35, 23) of each side channel (20, 21).
- Pump according to one of Claims 1-10, characterized in that one side wall (13) and the peripheral wall (14) are formed on an intermediate housing (15), which includes the pump outlet (17), and the other side wall (12) is formed on a housing cover (16), which includes the pump inlet (33) and is fixedly connected to the intermediate housing (15) and/or the pump housing (10).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19634900A DE19634900A1 (en) | 1996-08-29 | 1996-08-29 | Flow pump |
DE19634900 | 1996-08-29 | ||
PCT/DE1997/000760 WO1998009081A1 (en) | 1996-08-29 | 1997-04-15 | Feeding pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0857255A1 EP0857255A1 (en) | 1998-08-12 |
EP0857255B1 true EP0857255B1 (en) | 2002-11-20 |
Family
ID=7804000
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97922837A Expired - Lifetime EP0857255B1 (en) | 1996-08-29 | 1997-04-15 | Feeding pump |
Country Status (8)
Country | Link |
---|---|
US (1) | US6017183A (en) |
EP (1) | EP0857255B1 (en) |
JP (1) | JP2000500210A (en) |
KR (1) | KR19990067133A (en) |
CN (1) | CN1197504A (en) |
BR (1) | BR9706636A (en) |
DE (2) | DE19634900A1 (en) |
WO (1) | WO1998009081A1 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3638818B2 (en) * | 1999-05-20 | 2005-04-13 | 愛三工業株式会社 | Wesco type pump |
JP3800128B2 (en) * | 2001-07-31 | 2006-07-26 | 株式会社デンソー | Impeller and turbine fuel pump |
US6669437B2 (en) * | 2001-10-04 | 2003-12-30 | Visteon Global Technologies, Inc. | Regenerative fuel pump with leakage prevent grooves |
US6890144B2 (en) * | 2002-09-27 | 2005-05-10 | Visteon Global Technologies, Inc. | Low noise fuel pump design |
US7722311B2 (en) * | 2006-01-11 | 2010-05-25 | Borgwarner Inc. | Pressure and current reducing impeller |
DE102007018820A1 (en) * | 2007-04-20 | 2008-10-23 | Robert Bosch Gmbh | delivery unit |
US20140169960A1 (en) * | 2011-10-13 | 2014-06-19 | Mitsubishi Electric Corporation | Fuel pump |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3095820A (en) * | 1960-02-29 | 1963-07-02 | Mcculloch Corp | Reentry rotary fluid pump |
DE4020521A1 (en) * | 1990-06-28 | 1992-01-02 | Bosch Gmbh Robert | PERIPHERAL PUMP, ESPECIALLY FOR DELIVERING FUEL FROM A STORAGE TANK TO THE INTERNAL COMBUSTION ENGINE OF A MOTOR VEHICLE |
DE9104728U1 (en) * | 1991-04-18 | 1992-08-20 | Robert Bosch Gmbh, 7000 Stuttgart | Unit for pumping fuel from a storage tank to the internal combustion engine of a motor vehicle |
JP3107438B2 (en) * | 1992-01-14 | 2000-11-06 | 三菱電機株式会社 | Electric fuel pump |
DE4243544C2 (en) * | 1992-12-22 | 2003-04-17 | Bosch Gmbh Robert | Fuel Supply |
JP3237360B2 (en) * | 1993-02-04 | 2001-12-10 | 株式会社デンソー | Regenerative pump and its casing |
DE4338677C2 (en) * | 1993-02-05 | 1999-07-29 | Mannesmann Vdo Ag | Pump for conveying fluid, in particular as a fuel delivery unit for motor vehicles |
DE4318122C2 (en) * | 1993-06-01 | 2002-01-17 | Bosch Gmbh Robert | Unit for delivering fuel from a storage tank to the internal combustion engine of a motor vehicle |
JP3463356B2 (en) * | 1994-06-30 | 2003-11-05 | 株式会社デンソー | Wesco pump |
DE4446537C2 (en) * | 1994-12-24 | 2002-11-07 | Bosch Gmbh Robert | liquid pump |
-
1996
- 1996-08-29 DE DE19634900A patent/DE19634900A1/en not_active Withdrawn
-
1997
- 1997-04-15 CN CN97190860A patent/CN1197504A/en active Pending
- 1997-04-15 JP JP10511143A patent/JP2000500210A/en active Pending
- 1997-04-15 BR BR9706636-2A patent/BR9706636A/en not_active IP Right Cessation
- 1997-04-15 DE DE59708770T patent/DE59708770D1/en not_active Expired - Fee Related
- 1997-04-15 US US08/983,595 patent/US6017183A/en not_active Expired - Fee Related
- 1997-04-15 WO PCT/DE1997/000760 patent/WO1998009081A1/en not_active Application Discontinuation
- 1997-04-15 EP EP97922837A patent/EP0857255B1/en not_active Expired - Lifetime
- 1997-04-15 KR KR1019980703079A patent/KR19990067133A/en not_active Application Discontinuation
Also Published As
Publication number | Publication date |
---|---|
KR19990067133A (en) | 1999-08-16 |
WO1998009081A1 (en) | 1998-03-05 |
CN1197504A (en) | 1998-10-28 |
US6017183A (en) | 2000-01-25 |
DE59708770D1 (en) | 2003-01-02 |
EP0857255A1 (en) | 1998-08-12 |
BR9706636A (en) | 1999-09-14 |
JP2000500210A (en) | 2000-01-11 |
DE19634900A1 (en) | 1998-03-05 |
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